Power transfer device for four-wheel drive vehicles

ABSTRACT

A power transfer device includes a planetary gear unit which includes a sun gear, a carrier, a ring gear, and a plurality of planet gears journaled on the carrier and in mesh with the sun and ring gears. The planetary gear unit is shiftable between first, second and third positions to establish a high speed four-wheel drive mode in the first position wherein the carrier is engaged with an input shaft, and the sun and ring gears are each engaged with a pair of coaxial output shafts to permit differential action between the output shafts. The planetary gear unit is arranged to establish a high speed four-wheel drive mode in the second position wherein the carrier is engaged with the input shaft and one of the output shafts, and the sun gear is engaged with the input shaft and the other output shaft to restrict the differential action and is further arranged to establish a low speed four-wheel drive mode in the third position wherein the sun gear is engaged with the input shaft, the carrier is engaged with the output shafts, and the ring gear is locked to restrict the differential action.

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a power transfer devide for four-wheel drive vehicles, and more particularly to a power transfer device of the type which includs a planetary gear unit arranged to be shifted between high and low-range conditions to establish torque proportioning and locked-up reduction drive modes.

2. Description of the Prior Art

In U.S. Pat. No. 4,074,591 granted to Dick on Feb. 21, 1978, there has been proposed a shift mechanism for the planetary gear unit which may be shifted to establish a high-range mode wherein the carrier acts as an input member and the sun and ring gears as output members to establish torque proportioning differential action. The shift mechanism may be further shifted to establish a low-range mode wherein the sun gear acts as an input member, the ring gear as a reaction member, and the carrier as an output member to provide locked-up reduction drive.

The shift mechanism includes a pair of shifting sleeves which are axially slidably mounted on an input shaft and one output shaft and which are linked together by a ring such that they are slidable as a unit but rotatable relative to one another. The shifting sleeves each support thereon a floating collar. The other output shaft is in the form of a hollow shaft arranged in surrounding relationship with the input shaft. In the high-range mode, one of the shifting sleeves engages the input shaft with the carrier, and its associated floating collar engages the sun gear with the other output shaft. The other sleeve engages the ring gear with the one output shaft, and its associated floating collar is disengaged. In the low-range mode, the one sleeve engages the input shaft with the sun gear, and its associated floating collar engages the carrier with the other output shaft. The other sleeve engages the carrier with the one output shaft, and its associated floating collar locks the ring gear to the housing.

In a practical embodiment of such a power transfer device as described above, it is desirable that the planetary gear unit is further arranged to establish a high-range mode under restriction of the differential action so as to enhance driving performance of the vehicle on a road covered with snow.

SUMMARY OF THE INVENTION

It is, therefore, a primary object of the present invention to provide an improved power transfer device wherein the planetary gear unit is shifted between three positions to establish a high speed four-wheel drive mode under torque proportioning differential action and to establish high and low speed four-wheel drive modes under restriction of the differential action.

Another object of the present invention is to provide an improved power transfer device, having the above-described characteristics, wherein the shifting operation of the planetary gear unit is effected in a simple construction without the provision of any clutch sleeve.

A further object of the present invention is to provide an improved power transfer device, having the above-described characteristics, capable of eliminating loads acting on teeth of the gear parts of the planetary gear unit during restriction of the differential action.

According to the present invention briefly summarized, there is provided a power transfer device which comprises a housing, an input shaft rotatably mounted within the housing for drive connection to the output shaft of a power transmission, a first output shaft rotatably mounted within the housing in a coaxial relationship with the input shaft, a second output shaft rotatably mounted within the housing in a concentric relationship with the input shaft, and a planetary gear unit including a sun gear, a carrier, a ring gear, and a plurality of planet gears journaled on the carrier and in mesh with the sun and ring gears and being axially slidably mounted on the input and output shafts.

The planetary gear unit is shiftable between first, second and third positions to establish a high speed drive mode in the first position wherein the carrier is engaged with the input shaft, and the sun and ring gears are each engaged with the output shafts to permit differential action between the output shafts, the planetary gear unit being arranged to establish a high speed drive mode in the second position wherein the carrier is engaged with the input shaft and the first output shaft, and the sun gear is engaged with the input shaft and the second output shaft to restrict the differential action between the output shafts and being further arranged to establish a lock-up reduction drive mode in the third position wherein the sun gear is engaged with the input shaft, the carrier is engaged with the output shafts, and the ring gear is locked by engagement with the housing to restrict the differential action between the output shafts.

BRIEF DESCRIPTION OF THE DRAWINGS

Additional objects, features and advantages of the present invention will be readily appreciated from the following detailed description of preferred embodiments thereof when considered with reference to the accompanying drawings, in which:

FIG. 1 is schematic illustration of a preferred embodiment of a power transfer device in accordance with the present invention;

FIGS. 2 to 5 each are a sectional view showing details of the component parts of a planetary gear unit shown in FIG. 1;

FIG. 6 is a schematic illustration of another preferred embodiment of a power transfer device in accordance with the presert invention; and

FIGS. 7 to 10 each are a sectional view showing details of the component parts of a planetary gear unit shown in FIG. 6.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

In FIG. 1 of the drawings, there is schematically illustrated a preferred embodiment of a power transfer device in accordance with the present invention which is drivingly connected to the output shaft of a power transmission (not shown) in an associated automotive vehicle. The power transfer device includes an input shaft 11 for drive connection to the output shaft of the power transmission, a first output shaft 12 for drive connection to a rear-wheel propeller shaft (not shown), second and third output shafts 13 and 14 for drive connection to a front-wheel propeller shaft (not shown), and a plantary or epicyclic gear unit 20 axially slidably mounted on the input and output shafts 11, 12, 13.

The input and output shafts 11 and 12 are rotatably mounted within a housing 15 in a coaxial relationship and coupled at their inner ends with each other for relative rotation. The second output shaft 13 is in the form of a hollow shaft which is integrally formed with a drive sprocket 13a and rotatably mounted in place within the housing 15 in a surrounding relationship with the input shaft 11. The third output shaft 14 is integrally provided within a driven sprocket 14a and rotatably mounted within the housing 15 in parallel with the input and output shafts 11 and 13. The second and third output shafts 13 and 14 are drivingly connected to each other by means of a chain 16 stretched over the drive and driven sprockets 13a and 14a. The third output shaft 14 is further drivingly connected to the front-wheel propeller shaft.

The planetary gear unit 20 includes a sun gear 21, a ring gear 22, a carrier 23 and a plurality of planet gears 24 journaled on the carrier 23. As shown clearly in FIG. 2, the sun gear 21 has an internal spline 21a in meshing engagement with an external spline 13b of output shaft 13 and engageable with an external spline 11a of input shaft 11. The ring gear 22 includes a first annular spline piece 25 rigidly secured thereto which has an internal spline 25a in meshing engagement with an external spline 12a of output shaft 12 and an external spline 25b engageable with an internal spline 17a of a second annular spline piece 17 rigidly secured to an inner wall of the housing 15. The carrier 23 includes a third annular spline piece 26 rigidly secured thereto and has an internal spline 23a in meshing engagement with the external spline 11a of input shaft 11 and engageable with the external spline 12a of output shaft 12. The third annular spline piece 26 has an internal spline 26a engageable with the external spline 13b of output shaft 13.

The planetary gear unit 20 is arranged to be shifted between four positions respectively illustrated in FIGS. 2, 3, 4 and 5. For shifting the planetary gear unit 20, the first annular spline piece 25 is formed with an annular groove 25c which is coupled with a manually operated shift fork (not shown). Assuming that the planetary gear unit 20 is retained in the position shown in FIG. 2, the sun gear 21 is maintained in engagement with the second output shaft 13, the ring gear 22 is maintained in drive connection to the first output shaft 12 through the spline piece 25, and the carrier 23 is maintained in engagement with the input shaft 11. In such a condition, the carrier 23 acts as an input member to transfer the power from input shaft 11 to the first output shaft 12 through the planet and ring gears 24 and 22 and to the second output shaft 13 through the planet and sun gears 24 and 21. In this instance, the sun and ring gears 21 and 22 act as output members to establish torque proportioning differential action between the output shafts 12 and 13. Thus, the output shafts 12 and 13 are driven substantially at the same rotational speed as that of the input shaft to establish a high speed four-wheel drive mode under the differential action.

When the planetary gear unit 20 is shifted to and retained in the position shown in FIG. 3, the sun gear 21 is maintained in engagement with the input and output shafts 11 and 13, the ring gear 22 is maintained in drive connection to the first output shaft 12 through the first annular spline piece 25, and the carrier 23 is maintained in engagement with the input and output shafts 11 and 12 and in drive connection to the second output shaft 13 through the third annular spline piece 26. In such a condition, the sun gear 21, ring gear 22 and carrier 23 are connected with each other through the shafts 11-13 to restrict the differential action between the output shafts 12 and 13. Thus, the sun gear 21 and carrier 23 act as input members to transfer the power from input shaft 11 to the first and second output shafts 12 and 13 therethrough. As a result, the output shafts 12 and 13 are driven substantially at the same rotational speed as that of the input shaft 11 to establish a high speed four-wheel drive mode under restriction of the differential action between the output shafts 12 and 13.

When the planetary gear unit 20 is shifted to and retained in the position shown in FIG. 4, the sun gear 21 is maintained in engagement with the input shaft 11, the carrier 23 is maintained in engagement with the first output shaft 12 and in drive connection to the second output shaft 13 through the third annular spline piece 26, and the ring gear 22 is disengaged. In such a condition, the carrier 23 is positioned to permit free rotation of the sun, planet and ring gears 21, 24 and 22. Thus, the power from input shaft 11 may not be transferred to the output shafts 12 and 13. This is effective to maintain the power transfer device in a neutral condition.

When the planetary gear unit 20 is shifted to and retained in the position shown in FIG. 5, the sun gear 21 is maintained in engagement with the input shaft 11, the ring gear 22 is locked by engagement with the second spline piece 17 through the first spline piece 25, and the carrier 23 is maintained in engagement with the first output shaft 12 and in drive connection to the second output shaft 13 through the third spline piece 26. In such a condition, the sun gear 21 acts an input member, the ring gear 22 as a reaction member, and the carrier 23 as an output member to provide locked-up reduction drive. Thus, the power from input shaft 11 is transferred to the carrier 23 through the sun and planet gears 21 and 24, and subsequently the carrier 23 acts to transfer the power to the output shafts 12 and 13 therethrough. As a result, the output shafts 12 and 13 are driven by the input shaft 11 at a reduction speed ratio to establish a low speed four-wheel drive mode under restriction of the differential action between the output shafts 12 and 13.

From the above description, it will be understood that in the power transfer device, the high and low speed four-wheel drive modes are selectively established by shifting operation of the the planetary gear unit 20. This is effective to more enhance driving performance of the four-wheel drive vehicle. Furthermore, the neutral condition of the power transfer device is provided by shifting operation of the planetary gear unit 20. It is, therefore, able to adapt the power transfer device to an industrial vehicle equipped with a power take-off device. Additionally, it will be understood that the shifting operation of the planetary gear unit 20 is effected without the provision of any clutch sleeve. This is useful to reduce the component parts of the power transfer device so as to simplify the construction of the same. In the power transfer device, it is to be noted that the component parts of the planetary gear unit 20 are selectively engaged at their internal or external splines with the external splines of shafts 11-13 or the internal spline of second spline piece 17. This is useful to eliminate loads acting on the teeth of the respective gear parts 21, 22, 24 during restriction of the differential action.

In FIG. 6 there is schematically illustrated another preferred embodiment of a power transfer device in accordance with the present invention which is drivingly connected to the output shaft of a conventional power transmission (not shown) in an associated automotive vehicle. The power transfer device includes first and second input shafts 31 and 32 for drive connection to the output shaft of the power transmission, a first output shaft 33 for drive connection to a front-wheel propeller shaft (not shown), a second output shaft 34 for drive connection to a rear-wheel propeller shaft (not shown), and a planetary gear unit 40 axially slidably mounted on the input and output shafts 32, 33 and 34.

The first and second input shafts 31 and 32 are arranged in parallel to each other and rotatably mounted within a housing 35. The first input shaft 31 is integrally provided with a gear 31a which is in mesh with an idler gear 36a on an idler shaft 36, while the second input shaft 32 is integrally provided with a gear 32a which is in mesh with the idler gear 36a for drive connection to the gear 31a on input shaft 31. The idler shaft 36 is arranged between the input shafts 31 and 32 in parallel therewith and rotatably mounted within the housing 35. In this embodiment, the second input shaft 32 is in the form of a hollow shaft arranged in surrounding relationship with the first output shaft 33. The first and second output shafts 33 and 34 are rotatably mounted within the housing 35 in a coaxial relationship and coupled with each other at their inner ends for relative rotation.

The planetary gear unit 40 includes a sun gear 41, a ring gear 42, a carrier 43 and a plurality of planet gears 44 journaled on the carrier 43. As shown clearly in FIG. 7, the sun gear 41 has an internal spline 41a in meshing engagement with an external spline 33a of output shaft 33 and engageable with an external spline 32b of input shaft 32. The ring gear 42 includes a first annular spline piece 45 rigidly secured thereto which has an internal spline 45a in meshing engagement with an external spline 46a of a second annular spline piece 46 mounted on the second output shaft 34 for rotation therewith. The ring gear 42 is further formed thereon with an external spline 42a which is arranged to be engaged with an internal spline 37a of a third annular spline piece 37 rigidly secured to an inner wall of the housing 35. The carrier 43 has an internal spline 43a in meshing engagement with the external spline 32b of input shaft 32. The carrier 43 includes a fourth annular spline piece 47 rigidly secured thereto which has an internal spline 47a engageable with an external spline 34a of output shaft 34.

The planetary gear unit 40 is arranged to be shifted between four positions respectively shown in FIGS. 7, 8, 9 and 10. For shifting the planetary gear unit 40, the annular spline piece 45 is formed with an annular groove 45b which is coupled with a manually operated shift fork (not shown). Assuming that the planetary gear unit 40 is retained in the position shown in FIG. 7, the sun gear 41 is maintained in engagement with the first output shaft 33, the ring gear 42 is maintained in drive connection to the second output shaft 34 through the annular spline pieces 45 and 46, and the carrier 43 is maintained in engagement with the second input shaft 32. In such a condition, the carrier 43 acts as an input member, and the sun and ring gears 41 and 42 act as output members to transfer the power from input shaft 32 to the output shafts 33 and 34 therethrough. Thus, the output shafts 33 and 34 are driven substantially at the same rotational speed as that of the input shaft 32 to establish a high speed four-wheel drive mode under differential action between the output shafts 33 and 34.

When the planetary gear unit 40 is shifted to and retained in the position shown in FIG. 8, the sun gear 41 is maintained in engagement with the input and output shafts 32 and 33, the carrier 43 is maintained in engagement with the input shaft 32 and in drive connection to the second output shaft 34 through the spline piece 47, and the spline piece 45 is disengaged from the spline piece 46 on output shaft 34. In such a condition, the sun gear 41 and carrier 43 are drivingly connected to each other through the shafts 32, 33 and 34 to restrict differential action between the shafts 33 and 34. Thus, the power from input shaft 32 is transferred to the first output shaft 33 through the sun gear 41 and to the second output shaft 34 through the carrier 43. This is effective to drive the output shafts 33 and 34 substantially at the same rotational speed as that of the input shaft 32 so as to establish a high speed four-wheel drive mode under restriction of the differential action.

When the planetary gear unit 40 is shifted to and retained in the position shown in FIG. 9, the sun gear 41 is disengaged from the first output shaft 33 and maintained in engagement with the input shaft 32, while the carrier 43 is maintained in drive connection to the first and second output shafts 33 and 34 through the spline piece 47. In such a condition, the carrier 43 is positioned to permit free rotation of the sun, planet and ring gears 41, 44 and 42. Thus, the power from input shaft 32 may not be transferred to the output shafts 33 and 34. This is effective to maintain the power transfer device in a neutral position.

When the planetary gear unit 40 is shifted to and retained in the position shown in FIG. 10, the sun gear 41 is maintained in engagement with the input shaft 32, the ring gear 42 is locked by engagement with the third annular spline piece 37, and the carrier 43 is maintained in drive connection to the first and second output shafts 33 and 34. In such a condition, the sun gear 41 acts as an input member, the ring gear 42 as a reaction member, and the carrier 43 as an output member to transfer the power from input shaft 11 to the output shafts 33 and 34 therethrough. Thus, the output shafts 33 and 34 are driven at a reduction speed ratio to establish a low speed four-wheel drive mode under restriction of the differential action between the output shafts 33 and 34.

Having now fully set forth structure and operation of preferred embodiments of the concept underlying the present invention, various other embodiments as well as certain modifications and variations of the embodiments shown and described herein will obviously occur to those skilled in the art upon becoming familiar with said underlying concept. It is to understood, therefore, that within the scope of the appended claims, the invention may be practiced otherwise than as specifically set forth herein. 

What is claimed is:
 1. A power transfer device for four-wheel drive vehicles, comprising:a housing; an input shaft rotatably mounted within said housing for drive connection to an output shaft of a power transmission; a first output shaft rotatably mounted within said housing in a coaxial relationship with said input shaft; a second output shaft rotatably mounted within said housing in a concentric relationship with said input shaft; and a planetary gear unit including a sun gear, a carrier, a ring gear, and a plurality of planet gears journaled on said carrier and in mesh with said sun and ring gears and being axially slidably mounted on said input and output shafts, wherein said planetary gear unit is shiftable between first, second and third positions to establish a high speed drive mode in the first position wherein said carrier is engaged with said input shaft, and said sun and ring gears are each engaged with said output shafts to permit differential action between said output shafts, said planetary gear unit being arranged to establish a high speed drive mode in the second position wherein said carrier is engaged with said input shaft and said first output shaft, and said sun gear is engaged with said input shaft and said second output shaft to restrict the differential action between said output shafts and being further arranged to establish a low speed drive mode in the third position wherein said sun gear is engaged with said input shaft, said carrier is engaged with said output shafts, and said ring gear is locked by engagement with said housing to restrict the differential action between said output shafts.
 2. A power transfer device as recited in claim 1, wherein said input shaft is coupled at an inner end thereof with an inner end of said first output shaft for relative rotation, and said second output shaft is in the form of a hollow shaft arranged in surrounding relationship with said input shaft.
 3. A power transfer device as recited in claim 1, wherein said input shaft is in the form of a hollow shaft arranged in surrounding relationship with said second output shaft, and said first output shaft is coupled at an inner end thereof with an inner end of said second output shaft for relative rotation.
 4. A power transfer device as recited in claim 1, wherein said sun gear has an internal spline engageable with an external spline formed on said input shaft and an external spline formed on said second output shaft, and said carrier has an internal spline engageable with the external spline on said input shaft and an external spline formed on said first output shaft, and wherein said ring gear includes an annular spline piece secured thereto which has an internal spline engageable with the external spline or said first output shaft and an external spline engageable with an internal spline of an annular spline piece secured to an inner wall of said housing, and said carrier includes an annular spline piece secured thereto which has an internal spline engageable with the external spline on said second output shaft.
 5. A power transfer device as recited in claim 1, wherein said sun gear has an internal spline engageable with an external spline formed on said second output shaft and an external spline formed on said input shaft, said carrier has an internal spline engageable with the external spline on said input shaft, and said ring gear has an external spline engageable with an internal spline of an annular spline piece secured to an inner wall of said housing, and wherein said carrier includes an annular spline piece secured thereto which has an internal spline engageable with an external spline formed on said first output shaft and the external spline on said second output shaft, and said ring gear includes an annular spline piece secured thereto which has an internal spline engageable with an external spline of an annular spline piece mounted on said first output shaft for rotation therewith. 